Signal responsive belt printer

ABSTRACT

A first solenoid angularly and incrementally moves a sprocket wheel spacingly to translocate a carriage for an endless belt of the printer to a printing station in a horizontal succession thereof. A second solenoid, in response to a carriage return signal, disables transmission of the force of the first solenoid to the carriage, and effects shunting of such force, through an interposer, to a mechanism for incrementally drawing a web from a supply coil a distance equal to line spacing. A rockable bail is adapted releaseably to secure the coil in a seat on a pivoted gate which is arranged for opening and closing a coil chamber in the printer. A pair of spreadable spaced apart bail extensions project from opposed arms of the bail and are aligned when untensioned to provide an axis for rotation for holding the coil in its seat. When spread, the extensions permit coil replacement in said seat. A pair of cams which are integral with a bracket defining the seat are followed by the arms of the bail when rocked for controlling the condition of the extensions. The belt of the printer is trained about an impactor and a sprocket wheel mounted on the carriage. A stepping motor is adapted, through the agency of a sprocket wheel, to align successive selected dies, carried longitudinally of the belt, for image transfer by the impactor at successive printing stations. A bracket supported by the carriage rocks in response to a third solenoid for driving the impactor into a printing mode in which the belt is tensioned. Restoration of the impactor to a non-print mode eases belt tension and thereby facilitates belt adjustment for die alignment for printing. A replaceable cartridge has an endless ribbon disposed between the belt and the web for printing. An inking roller carried in the cartridge is coupled to carriage movement during carriage translocation between line start and carriage return positions and for driving the ribbon. A clutch uncouples the inking roller during carriage return to the line start position.

United States Patent [191 Denley [451 Feb. 26, 1974 SIGNAL RESPONSIVE BELT PRINTER Ronald S. Denley, Niles, 111.

[75] Inventor:

[52] US. Cl 101/111, 101/93 C, 197/49, 197/57, 197/82, 197/133 R, 197/151, 197/168 [51] Int. Cl B41] 1/60 [58] Field of Search 101/93 C, 111; 197/49, 57, 197/133 R, 151, 168, 82

[56] References Cited UNITED STATES PATENTS 1,098,118 5/1914 Ireland 197/133 2,831,424 4/1958 MacDonald... 101/93 C 2,901,540 8/1959 Canepa 101/93 C UX 3,041,965 7/1962 Sasaki 101/111 3,045,796 7/1962 Scribner 197/57 3,224,366 12/1965 Cunningham 101/111 X 3,291,042 12/1966 Christoff et al 197/168 X 3,408,930 11/1968 Chamness et al.. 101/93 C 3,424,291 1/1969 Marion 197/49 3,429,414 2/1969 Bradbury 197/49 X 3,532,204 10/1970 Sasaki 197/82 X 3,561,581 .2/1971 Takenaka 197/49 3,621,968 ll/l97l Kondur 197/151 3,667,383 6/1972 Mack et a1. 101/93 C Primary Examiner-Ernest T. Wright, Jr. Attorney, Agent, or FirmSherman P. Appel; John L. Landis [57] ABSTRACT A first solenoid angularly and incrementally moves a sprocket wheel spacingly to translocate a carriage for an endless belt of the printer to a printing station in a horizontal succession thereof. A second solenoid, in

FIG. 12

response to a carriage return signal, disables transmission of the force of the first solenoid to the carriage, and effects shunting of such force, through an interposer, to a mechanism for incrementally drawing a web from a supply coil a distance equal to line spacing.

A rockable ball is adapted releaseably to secure the coil in a seat on a pivoted gate which is arranged for opening and closing a coil chamber in the printer. A pair of spreadable spaced apart bail extensions project from opposed anns of the bail and are aligned when untensioned to provide an axis for rotation for holding the coil in its seat. When spread, the extensions permit coil replacement in said seat. A pair of cams which are integral with a bracket defining the seat are followed by the arms of the bail when rocked for controlling the condition of the extensions.

The belt of the printer is trained about an impactor and a sprocket wheel mounted on the carriage. A stepping motor is adapted, through the agency of a sprocket wheel, to align successive selected dies, carried longitudinally of the belt, for image transfer by the impactor at successive printing stations. A bracket supported by the carriage rocks in response to a third solenoid for driving the impactor into a printing mode in which the belt is tensioned. Restoration of the impactor to a nomprint mode eases belt tension and thereby facilitates belt adjustment for die alignment for printing.

A replaceable cartridge has an endless ribbon disposed between the belt and the web for printing. An inking roller carried in the cartridge is coupled to carriage movement during carriage translocation between line start and carriage return positions and for driving the ribbon. A clutch uncouples the inking roller during carriage return to the line start position.

18 Claims, 19 Drawing Figures PATENIEDFEBZB I974 SHEET 1 BF 8 FIG.

INVENTOR RONALD S. DENLEY MKW PATENTEB FEBZ 81974 SHEET 3 OF 8 CL OE mm. 0 :N

Pmmmrmw: 3793.951

SHEEI 5 OF 8 FIG. 9

PATENTED FEB 2 SHEET 8 UF 8 388 \386 387 /382 A 6 FIG. I8 388' I 392 HI I :52 390 w I 1 3 l 38l I I46 STEP 391 MOTOR LOGIC 4|| 401 398 v [4|O f ,404 4|4\ I 6 BIT UP-DOWN 'CARRAGE 7 COUNTER RETURN v 402- SWITCH 399 I [#396 Cons 395 6 BIT CONVERTER ADDER f 7 W407 388 389 246W 7 V {240 FUNCTION SPACE PRINT SOL. SOL. SOL

389 FIG. I9

SIGNAL RESPONSIVE BELT PRINTER FIELD OF THE INVENTION The present invention relates to signal controlled printing. Particularly, it relates to teleprinters adapted for use in mobile installations.

Signal controlled printers are widely employed in various applications to transcribe messages that are received in the form of electrical signals. In addition to their widespread use in stationary installations, a considerable need also exists for such printers in mobile installations. For example, teleprinters in various vehicles would considerably improve the accuracy of communication with remote offices and also provide a permanent record of messages. Such installations have been proposed, for example, in police work, as well as in many other fields.

Although prior printers heretofore have been employed effectively in mobile units, their relatively large size has curtailed wide use in vehicles, such as automobiles. It is the primary object of the present invention to minify signal controlled printers. It is another object of the invention to enable easy use of printers of the indicated class in vehicles, such as automobiles.

Reducing printer size in accordance with the present invention results from minimizing the number of printer parts. The attendant benefit of reduced printer costs is calculated to encourage wider printer usage. Development of improved systems adapted for combination in a signal controlled printer have enabled attainment of the foregoing, and other objects of the invention which will be apparent from the ensuing detailed description. The features of said systems include (1) improved web handling means enabling web loading with one hand, (2) an improved ribbon and inking mechanism assembled in a disposable cartridge, (3) novel though simplified station spacing and line feed mechanisms, and (4) an improved impactor and die carrier assembly for printing in a small belt printer.

SUMMARY OF THE INVENTION From one aspect, the invention is embodied in an impact printer which comprises an endless belt disposed in a circuit, the belt having a plurality of dies spaced apart longitudinally of the circuit. Impacting means are mounted for successively urging the belt into a printing mode at successive printing stations. Means are adapted for moving the belt circuitously for successively aligning selected dies with the impacting means for printing. Means are provided for translocating said belt and said impacting means simultaneously to successive printing stations. Means are also provided for replaceably supporting a web coil and for spending the web from the coil successive line spacing distances. The power stroke of a lineally reciprocative member is impinged on the translocating means and the spending means for selectively spacing the belt and feeding the web.

From yet another aspect, the invention is an impact printer wherein an impactor is movable into and out of a printing mode and is supported on a carriage arranged for reversible lineal translocation in a path to successive stations between line start and carriage return positions. An endless ribbon is driveable in a circuitous path for aligning successive ribbon segments with the impactor for printing. Means couple the ribbon driving means to the carriage movement.

From a still further aspect, the invention is embodied in an impact printer having printing means which comprises an endless belt trained about a drive roller and an impacting roller for moving the belt in a circuitous path to present successive selected dies on the external surface of the belt at successive aligned printing stations for printing. The impacting roller is rockable between a belt tensioned condition, when a selected die is in a printing mode, and a belt eased condition, upon removal of a selected die from a printing mode; and the belt is movable for presenting a selected die for printing while the belt is in its eased condition.

BRIEF DESCRIPTION OF THE DRAWING In the ensuing detailed description, reference is had to the accompanying drawing in which:

FIG. 1 is a perspective view of a belt printer in accordance with the present invention, portions of the printer housing being broken away;

FIG. 2 is a vertical sectional view of the printer taken according to the line 2-2 in FIG. 1;

FIG. 3 is a detailed view of fastening means taken according to the line 33 in FIG. 2;

FIG. 4 is a partial vertical sectional view taken according to the broken line 44 in FIG. 2;

FIG. 5 is a view of web managing means for the printer with a part broken away and in the same plane as, however, alternately conditioned from the condition of FIG. 2, an alternate relative position of another part being shown in dashed lines;

FIG. 6 is a view of the web managing means taken according to the line 6--6 in FIG. 5, parts being broken away;

FIG. 7 is a detailed view of a portion of the web managing means taken according to the line 7-7 in FIG.

FIG. 8 is a view of carriage spacing and line feeding means taken in a vertical plane according to the line 8--8 in FIG. 4;

FIG. 9 is a view of the carriage spacing and line feeding means taken according to the line 99 in FIG. 8, parts being broken away;

FIG. 10 is another view of the carriage spacing and line feeding means taken in a vertical plane according to the line l0-l0 in FIG. 8;

FIG. 11 is a detailed view of means for abating noise resulting from solenoid operation in the printer;

FIG. 12 is a top plan view of a carriage in said printer, a portion of a platen being broken away, taken along line 12-12 in FIG. 4;

FIG. 13 is a view similar to FIG. 12; however, showing a disposable ribbon cartridge mounted on the carriage, the top of the cartridge having been removed;

FIG. 14 is a view taken in a vertical plane according to the line l4--14 in FIG. 13;

FIG. 15 is a detailed view of the ribbon cartridge according to the line 15-15 in FIG. 13;

FIG. 16 is a detailed view taken according to the line 16-16 in FIG. 13;

FIG. 17 is a plan view taken according to the line l7-l7 in FIG. 14;

FIG. 18 is an electrical scheme of a circuit for operating the printer; and

FIG. 19 is an electrical scheme of a sensor associated in the circuit.

DETAILED DESCRIPTION OF THE ILLUSTRATED PRINTER Referring now to the drawing, particularly to FIG. 1, shown is a signal controlled belt printer 20. It is less than the width of an adult human body and is proportioned to be hung over the front bench from the bench back in an automobile of standard size. The printer has a housing 22 comprised of an upper section 30 and a lower section 32. A rotationally mounted knurled knob 24 projects through an aperture 23 in an upper sloping flat surface 25 of upper housing section 30 for manually controlling a platen 26 (FIG. 2). A shaft 27 (FIGS. 9 and which supports the platen 26 is journalled in an upper frame member 78 of the printer framework. An on-off switch, of which only a manual member 28 (FIG. 1) is shown, projects through another aperture 29 in surface 25.

Surface 25 has an opening 34 in which a transparent shield 36, which partially occludes said opening 34, is mounted. A tear edge 38 of the shield 36 is spaced from the upper side of said opening 34 to provide a slot or passage 40 for moving the downstream end portion of a web 42 or carrier for records out of housing 22. Within the housing 22, the web 42 is supplied from a roll or coil 44 (FIGS. 2, 4, 5, and 6) and extends along a path 43.

A pressure roller 48, concentric with its support shaft 46, carries a pair of laterally spaced apart friction bearings, herein shown as O-rings 50 (FIGS. 1, 2, and 4). They are arranged for holding the web 42 against platen 26 in a customary fashion. Accordingly, the support shaft 46 extends laterally; and it is hung with a horizontal aspect from a pair of frame extensions 47, a nut 49 securing the support shaft 46 to said frame extensions 47.

A printing mechanism, generally designated 52 (FIGS. 1 and 2), is comprised of a carriage 54 arranged for reversible movement in a path extending laterally of printer between a place of beginning or line start station at the left (FIG. 1) of housing 22 to a line end or carriage return station at the right of the housing 22. A rear rail 56 and a forward or front rail 57 facilitate carriage movement. They are spaced apart in a horizontal plane and extend laterally of housing 22, with opposed rail end portions being secured by fasteners 55 (FIG. 4) to upper frame member 78. A plurality of rollers 58, 59, and 60 guidingly couple the carriage 54 to said rails 56 and 57.

Roller 58 is a guide roller and has a circumferential groove 162 (FIG. 2) in which the upper portion of rear rail 56 is slidingly engaged. Roller 59 is cylindrical, engaging the under surface of rail 56, and with roller 58 prevents vertical displacement of carriage 54. Rollers 60 are also cylindrical, being similar to roller 59, and slideably engage front rail 57 from above and below. Fastening means 163 connects the rollers 60 to a forward portion of carriage 54; whereas, like fasteners 164 connect rollers 58 and 59 to the rear portion of said carriage 54.

A bumper 62 mounted on the left side (relative FIG. 1) of carriage 54 is adapted to damp the force resulting from carriage return in a manner which will be described hereinafter. Ink supply and ribbon control means 64 for printer 20 include a ribbon cartridge 66. The latter is disposable, being releasably retained on carriage 54 by means which will be ensuingly described.

In addition to upper frame member 78, the framework of printer 20 comprises a lower frame member (FIG. 2). The frame members 78 and 80 are rigidly secured together within housing 22 and by fastening means generally designated 82. A pair of opposed framework openings 77 (only one of which is seen in FIG. 8) are proportioned and disposed for enabling manipulation of frame member 78 and the structures connected to or hung therefrom. A cross tie 79 (FIGS. 2 and 8), which extends across the rear of apparatus, rigidifies the upper frame member 78.

For damping frame vibrations, fastening means 82 comprises a plurality of metal screw assemblies (exemplified in FIG. 3). A metal screw 84 associated in each of said assemblies projects through aligned apertures in both frame members 78 and 80. The screw 84 is threaded through member 80 to draw said frame members 78 and 80 together. A washer 85 is held in engagement with each screw head 87 by a first resilient ring 86, the ring 86 being disposed aboutthe shank of the screw 84 and arranged for compression against the washer 85 and frame member 78. A second resilient ring 88 is disposed about the shank of each screw 84 between frame members 78 and 80 and engaged with facing surfaces thereof. Cushioning of the frame members 78 and 80 is enhanced by a chamfered surface 90 which is formed in frame member 78 about the shank of the screw 84. Tightening ofa lock nut 92 on the free end of the screw 84 insures rigid association of the frame members 78 and 80 with ring 88 compressed therebetween and against the chamfered surface 90. Thereby, concentric location of the shank of the screw 84 is insured within frame member 78.

The framework divides the interior of the housing 22 into an upper chamber 74 and a lower chamber 76 (FIG. 2). Coil 44 is mounted in the latter chamber 76 for replacement when spent. Means for managing said coil 44 comprises a manually controllable door 68 (FIGS. 2 and 5). It is rockable about a pivot 70 in an opening 69 in housing 22 between a closed, first or vertical aspect (FIG. 2) in which the opening 69 is closed and an open, second or horizontal aspect (FIG. 5) in which the opening 69 is open.

A U-shaped bracket 94 has a pair of laterally spaced apart side plates 98 and 100, and a connecting section 102 (FIGS. 2, 4, and 5) with a tongue or extension 104. The connecting section 102 and said tongue 104 are secured to the inside flat of door 68 for securing the bracket 94 thereto with side plates 98 and extending perpendicularly. Accordingly, a web coil 44 mounted on said bracket 94 will follow the door 68, an opening 96 in frame member 80 enabling such coil 44 to be rocked between a loading position in which the door 68 is open and a printing position in which the door 68 is closed.

A tongue 106 is struck inwardly from bracket 94 at the juncture of connecting section 102 and tongue 104. The tongue 106 and side walls 98 and 100 define a coil seat 108. The tongue 106 is disposed and proportioned such that its inner edge 110 will cause a full coil 44 to be seated with its coil supporting cylinder 126 (FIG. 6) aligned in an axial position for enabling coil rotation for web 42 removal in a manner which will ensuingly be described.

Side plates 98 and 100 have a pair of opposed, outwardly struck, horizontally aligned hubs 112 with center openings 114. The opposed ends of spaced apart axis lugs or extensions 1 16 of a squared C-shaped manually swingable spring bail 118 are engaged in the holes 114. The bail 118 has a pair of opposed flexible arms 120 from the ends of which the axis lugs 116 angularly project each generally toward the other. The arms 120 are integral with and connected to opposite ends of a bail connecting section 122 and are proportioned to space section 122 away from seat 108 and clear of side plates 98 and 100. In consequence of the foregoing arrangement, the bail 118 is rockable over seat 108, between a coil loading position (solid line of FIG. 5) and a printing or web retained position (dashed line of FIG. 5).

Opposed arms 120 are disposed in following engagement with corresponding camming edges 123 of a pair of tapered flanges or cams 124 along which the arms 120 slide as bail 118 is swung. Each of the cams 124 projects outwardly from one of side plates 98 and 100 and has a wide part 130 (FIGS. 6 and 7) and a narrow part 132.

The proportioning of parts is such that when arms 120 are disposed in engagement with the narrow parts 132, the arms 120 will be relaxed or untensioned; and axis lugs 116 will be coaxially and horizontally aligned, and though spaced apart, they will be unspread. Thusly conditioned, the axis lugs 116 are adapted for engagement in opposed end openings of the supporting cylinder 126 for coil 44. Thereby, the axis lugs 116 comprise means for enabling coil rotation, for uncoiling or spending the coil 44 as web 42 is fed a line at a time and for preventing coil removal from seat 108. On the other hand, when arms 120 are disposed in engagement with wide parts 130, the arms 120 are tensioned and spread; and the axis lugs 116 will correspondingly spread, disaligned, and out of cylinder 126 (FIG. 6), though retained in hubs 112. Thereby, a coil 44 can be replaced in seat 108, provided door 68 is open.

Moreover, the arrangement of parts is such that, when the lugs 116 are in spaced condition, bail section 122 will have been moved from over seat 108 enabling coil replacement. However, when the lugs 116 are in untensioned or printing position, said bail section 122 is disposed over the seat 108, further preventing coil removal.

A pair of opposed detenting notches 128 (FIGS. 6 and 7) in the wide part 130 of cams 124, are adapted to releaseably hold bail 118 in loading position whereby coil replacement is facilitated. Once a new coil 44 has been inserted in seat 108, it is readily locked into the chamber 76 and the bail 118 restored to coil retaining position by manually releasing arms 120 from the detenting notches 128.

A pair of expansion springs 134 then, under tension, restore bail 1 18 to coil retaining condition. Each of said springs 134 is disposed adjacent one of the sides 98 and 100 and has an inner end anchored on a lug 136 which is secured to door 68, and an outer end connected to a lug 138 which is secured to each arm 120. Additionally, the springs 134 damp web moving force during line feed. To that end web 42 is routed in course 43 between bail 118 and bracket 94, the web 42 supporting the bail (FIG. 2).

Carriage 54 comprises a U-shaped strap 140 (FIGS. 2 and 4) and a horizontally disposed motor hanger,

hanger or mounting plate 144. Extension 142 of said mounting plate 144 is secured to the strap by means of the fasteners 164 which also secure rollers 58 and 59 to carriage 54.

The mounting flange 147 of a stepping motor 146 is secured to plate 144 by fasteners 148 (FIG. 12) and thereby suspends the motor 146 from the plate 144. The hub 150 of a sprocket wheel 152 is secured by a fastener 154 (FIG. 2) to the output shaft 149 of said motor 146 above plate 144. An endless flexible sprocket belt 156, comprising printing means, carries a plurality of printing dies 157 (FIG. 18) on its outer surface, the dies 157 being spaced apart uniformly longitudinally of said belt 156. The belt 156 is trained in a circuitous path in a horizontal plane above plate 144, and about sprocket wheel 152 and a cylindrical impactor 158. The cylindrical impactor 158 functions as an idler sprocket for the belt 156 and is arranged for rotation about a pivot 159 (FIG. 12). Molded teeth 155 (FIG. 12) on the inner surface of belt 156 operably mesh in driven relationship with the sprocket wheel 152 and are guided by parallel flanges of the impactor 158.

In the exemplary embodiment, each angular position of belt 156 in its circuitous path corresponds to an angular condition of motor 146. Printing or image transfer is effected, a character at a time while carriage 54 is immobilized. Before each character is printed, the belt 156 is adjusted in its circuitous path, if required, for presenting a corresponding selected printing die 157 at a printing station and at a predetermined angular position relative to and adjoining impactor 158. Then the impactor 158 is driven toward platen 26 for transferring the image of such die 157 onto an aligned section of web 42 through a segment of an inking ribbon 160 then disposed between the belt 156 and the web 42.

Means for driving impactor 158 include an irregularly shaped lever 174 (FIGS. 12 and 13) which is rockably connected to hanger plate 144. Vertical axis means or a pivot 176 for effecting the connection extends through one end portion of a flat arm 175 of the lever 174 which is disposed above plate 44. Pivot 159 is carried from the other end portion of said arm 175. Thereby, impactor 158 and the portion of the belt 156 thereabout entrained are rockable adjacent the upper surface of plate 144 and about pivot 176 between a printing mode (solid line of FIG. 13) and a non-print mode (phantom line of FIG. 13).

Pivot 176 is disposed somewhat medially of output shaft 149 and pivot 159; and the parts are arranged such that said pivots 176 and 159 and the axis of shaft 149 are closest to alignment when the impactor 158 is in a printing mode. By reason thereof, belt 156 is highly tensioned during printing. However, as said belt 156 is rocked to a non-print mode, pivot 159 is moved away from such alignment and closer to shaft 149. Thereby, belt tension is relaxed, whereby belt movement for alignment of an ensuing die 157 is facilitated.

Means for rocking the impactor 158 between print and non-print modes comprises a boss or follower 180 (FIG. 12) in the form of a small plate fashioned below plate 144 and integrally with an end portion 178 of lever 174. A striker 182 carried from the end of a reciprocative arm 184 of a printing solenoid 186 (FIGS. 2 and 4) is arranged for pushing follower 180 during each power stroke of said solenoid 186. Thereby, the impactor 158 is rocked into a printing mode against the effect of a restoring spring 188 whose opposite ends are connected to an anchor 190 carried from plate 144 and an extension 192 from lever 174.

Means for spacing or stepping the carriage 54 to translocate printing means 52 to successive equally spaced apart and horizontally aligned printing stations include an offset flange 168 (FIG. 2) of strap 140. It is secured to an endless sprocket belt 170 by means comprised of a clamping plate 172 and a screw assembly 173. Moreover, said last belt 170 extends laterally of the framework in a horizontal plane. Laterally spaced apart idler and drive sprocket wheels 194 and 196 (FIGS. 2, 4, and 8) about which belt 170 is trained are disposed in a circuitous path in a vertical plane. The sprocket teeth of sprocket wheels 194 and 196 have a meshed relationship with molded teeth 171 (FIGS. 4 and 12) fashioned n the inner surface of belt 170.

An elongated laterally extending U-Shaped frame member 198, which is secured by a plurality of fasteners 200 (FIG. 8) to an extension of upper frame member 78, has a pair of laterally spaced apart bracket elements 197 and 199. As viewed from the front in FIG. 4, the bracket 197 is near the right end of the terminal and the bracket 199 near the left end, with the frame 198 extending across the entire length of the apparatus as shown in FIG. 4 and, in section, in FIG. 2. A shaft 202 for idler sprocket wheel 194 is journalled in bracket element 197. A shaft 204 of drive sprocket wheel 196 is secured in bracket element 199.

A ratchet wheel 206 (FIGS. 8, 9, and 10) included in the carriage spacing or stepping means comprises a transmission component in the means for driving belt 170. The ratchet wheel 206 is journalled on shaft 204 for transmitting carriage driving torque. To incrementally rotate the ratchet wheel 206, an arm 207 (FIG. 9) having a feed pawl 208 is mounted rockably about an axis defined by a pivot pin 210.

Means for operating feed pawl 208 comprises a linkage generally designated 212. The linkage 212 includes a V-shaped link 214 having a hub 216 journalled about shaft 204. An arm 218 of the link 214 which projects from hub 216 supports pin 210 through the agency of which link 214 is connected to arm 207. A moment arm 220 of link 214 is connected to the frame member 78 by tension spring 222. The arm 220 has a follower surface 223 along which a cam roller 224 is slideable. The roller 224 is carried from a lower end of a lever 234, and opposite to a pivot pin 235 about which lever 234 is rockable. The position of engagement of the cam roller 224 and said lever 234 determine the place of torque transfer from said lever 234 to arm 220 and accordingly said link 214.

A solenoid 240 (FIGS. 2 and 4) rocks lever 234 through the agency of a link or arm 226. The arm 226 has one end portion pivoted as at 232 to the lever 234 medially of roller 224 and pivot pin 235 and another end portion pivotally connected as at 230 to the lineally reciprocative member plunger or rod 228 of solenoid 240. An expansion spring 236 is arranged with one end portion attached to frame member 78 and an opposite end portion connected to a medial portion of said lever 234 for biasing the lever 234 clockwise with respect to FIG. 9. An expansion spring 238 having an end portion secured to link 214 and an opposite end portion connected to a medial portion of feed pawl 208 biases the pawl 208 into operative engagement with ratchet wheel 206.

Solenoid 240 is mounted in a frame 241 and has a lineal power'stroke (to the right with respect to FIG. 9) and a return stroke. A guide member 242 (FIGS. 2 and 4) for solenoid plunger 228 is supported on a plurality of spacers 243 and therewith secured to the U-shaped frame member 198 by the fasteners 200 (FIGS. 2 and 8). In consequence of the foregoing construction, upon actuation of solenoid 240, lever 234 rocks counter clockwise (relative to FIG. 9) against the restoring action of restoring spring 236 and causes cam roller 224 to move responsively along surface 223 toward shaft 204 thereby shortening the moment of arm 220. In turn, link 214, against the restoring action of spring 222, moves clockwise, its torque being transmitted to arm 207 which is drawn downwardly by expansion spring 238 for driving the feed pawl 208 downwardly for advancing ratchet wheel 206 one notch. Though the force of the solenoid 240 increases, thereby to increase the force on member 228 as the power stroke progresses, the shortening of the moment of arm 220 insures uniform transmittal to or application on pawl 208 of the varying force imposed on the plunger 228.

The parts are proportioned such that upon such advancement of the ratchet wheel 206, pulley wheel 196, which is secured to said ratchet wheel 206, moves a distance required to advance carriage 54 one step or printing space or column. Upon the deenergization of solenoid 240, lever 234 is restored to an untensioned condition by spring 236; and link 214 is restored by spring 222. As the last mentioned link 214 moves counterclockwise to its restored position, its torque is effective for moving arm 207 upwardly, thereby to disengage pawl 208 from between the teeth of ratchet wheel 206 and responsively to tension spring 238, when the ratchet wheel 206 is restrained in a manner which will I appear from the following description.

A check pawl 209 is rockable about a fixed axis pin 211. Said pin 211 is mounted in a bracket 213 (FIG. 8) which is fixed relative to frame member 78. The check pawl 209 is proportioned for engaging between the teeth of ratchet wheel 206 and for restraining or preventing ratchet wheel return (counterclockwise with respect to FIG. 9) while permitting clockwise motion of the ratchet wheel 206 in consequence of the feeding movement of pawl 208. Therefore, the check pawl 209 is adapted for preventing movement of carriage 54 toward line start position (to the left with respect to FIG. 4) though permitting carriage movement for spacing. A torsion spring 239 (FIG. 8) urges the check pawl 209 into holding engagement with the rachet wheel 206. It becomes tensioned as the check pawl 209 moves outwardly and slides over the ratchet teeth during feeding movement. However, it draws the check pawl 209 into ratchet holding engagement as the feed pawl 208 rocks in its reverse mode.

To enable carriage return to its line start station, a rockably mounted pawl kickout member or stripper 244 is aligned with the lower end portions of arm 207 and the check pawl 209. The stripper 244 comprises a lower end extension of a lever 245, and is responsive to a function solenoid 246 (FIGS. 8, 9, and 10) whose power stroke is up (with respect to FIG. 10). The arrangement is such that as lever 245 is rocked counterclockwise (from its position of FIG. 9), the stripper 244 will engage arm 207 and check pawl 209 and move them a distance sufficient to prevent their engagement with ratchet wheel 206, thereby permitting carriage return to its line start position.

Function solenoid 246 is mounted in a bracket 247 (FIG. 8). The bracket 247 is secured to tie 79 and upper frame member 78 by a plurality of fasteners 248. The plunger 249 of said solenoid 246 is connected by a pivot 250 to one end portion of a straight arm 251, the arm 251 being connected at its other end portion by a pivot 252 to a medial extension 253 of lever 245 whose main portion is spaced from arm 251. A pivot 254 for lever 245 is disposed such that upon energization of solenoid 246, said lever 245 will be rocked clockwise (relative to FIG. 10) to its kick-out or stripping position.

The upper end portion of the lever 245 is connected by a pivot 256 to an interposer 258 fashioned as an arm. Accordingly, the interposer 258 will be driven to the right (relative to FIG. 10) during the power stroke of solenoid 246. A rod 260 carried from interposer arm 258 is proportioned and arranged such that upon energization of said solenoid 246, the interposer rod 260 will move into alignment with a striker 262 (dotted line position of FIG. 9). The striker 262 rocks responsively to solenoid 240 as it is carried from an extension 263 of lever 234. The rod 260 and the striker 262 are proportioned such that as lever 234 rocks counterclockwise (relative FIG. 9) when the interposer rod 260 is in said dotted line position, the rod 260 will be driven downwardly, thereby to rock arm 258 counterclockwise. In the absence of the movement of the interposer 258, however, when solenoid 240 is actuated, the striker 252 is ineffective for any purpose. Accordingly, energy of solenoid 240 is shunted to arm 258 only when the function solenoid 246 has been energized.

A barrel roller or bearing 264 carried on an outer end portion of arm 258 rides on a medial extension 266 of a line feed lever 267. A body portion of the line feed lever 267 is disposed transversely of the medial extension 266 and has one end portion connected about a fixed pivot 268 (FIG. 8) and an opposite end portion pivotally connected, as indicated by the numeral 269', to the lower end portion of a line feed pawl 270. The roller 264 is proportioned and arranged for sliding alternately to the left and to the right (with respect to FIG. 9) on extension 266 during each cycle of solenoid 246. It is also adapted to drive downwardly against extension 266 upon actuation of rod 260 by striker 262 for rocking lever 267 counterclockwise (relative to FIG. 8).

Pawl 270 has an operative relationship with a ratchet 272 such that when function solenoid 246 is actuated, said pawl 270 will be drawn downwardly and into driving engagement with the teeth of said ratchet 272. The ratchet 272 is incrementally rotatable being secured on shaft 27, the parts being proportioned such that for each stroke of the pawl 270, the ratchet 272 will move an angular distance equal to the displacement of web 42 one line in a downstream direction.

Pawl 270 has a follower surface 269 (FIG. 8) for movement along an arcuate surface of a fixed roller cam 271. The center of the cam 271 is spaced from an anchoring extension 273 on the pawl 270 to which one end of a pawl expansion spring 274 is anchored. A toggle type arrangement of the parts generates maximum spring tension when the cam center and extension 273 are most widely spaced; pawl 270 then being in centered position. In a first of its over center positions, the pawl 270 is biased into operative engagement with ratchet 272. In its second over center position (FIG. 8), pawl 272 is biased out of ratchet engagement. The power and return strokes of solenoid 246 are adequate to overcome maximum tension of spring 274. In consequence, upon energization of said solenoid 246, the pawl 272 will move to its first over center or line feed position; and upon deenergization of said solenoid 246, the pawl 272 will be rocked out of ratchet engagement and move into its second over center position.

A check pawl 276 (FIG. 8) is rockable about a fixed pivot 278 and has a lower extension 280 fashioned with a hook 281. An expansion spring 282 anchors in said hook 281 and biases the check pawl 276 toward ratchet 272. The pawl 276 is proportioned for engaging between the teeth of said ratchet 272 and for preventing counterclockwise ratchet movement (relative to FIG. 8). It is also proportioned for slipping over the ratchet 272 to permit ratchet movement for line feeding of web 42. The foregoing arrangement permits manual adjustment of platen 26 by rotation of knob 24 clockwise with respect to FIG. 8.

Though the power stroke of solenoid 246 is effected against the action of a restoring spring 283 (FIGS. 8 and 10), further damping to minimize noise may be required. To that end, plunger 249 has a head 284 with a conically tapered neck 286. Dampening means comprising an O-ring 290 (FIG. 11) is disposed about the neck 286 in engagement with a shoulder 288 which defines an opening 291 in the solenoid assembly in which plunger 249 is reciprocative. The parts are proportioned such that the compression force of the O-ring 290 matches the force of the power stroke of the solenoid 246 at about the time head 284 would tend to engage the frame 289 of solenoid 246.

Carriage return means comprises a coil or clock spring 292 (FIG. 4) having an end portion 293 which extends through a curved guide 295 and is rigidly secured relative to the left side of upper frame member 78. The guide 295 extends between the left end portions of rails 56 and 57 and is rigidly secured by any suitable means to the left side of the upper frame member 78. The spring 292 has another end portion 297 journalled on post 296 about which the spring 292 is coilable. The post 296 in turn is secured to carriage 54 transversely of said rails 56 and 57. Thereby, as the carriage 54 moves toward its line start station, the spring 292 will coil. As it moves in an opposite direction, the spring 292 will uncoil and become tensioned for carriage return.

A bridge 300 which extends transversely of rails 56 and 57 has a pair of rail passing apertures 301 and 302 (FIG. 8). An abutment pad 304 is secured to the right hand surface of the bridge 300 medially of the apertures 301 and 302 in alignment with bumper 62 (FIG. 1 A pneumatic cylinder 306 having an axis extending longitudinally of said rails 56 and 57 has a right end portion which is secured to the left surface of said bridge 300. The cylinder 306 has a left end portion through which its plunger 308 projects longitudinally of said rails 56 and 57, the outer end portion of said plunger 308 being rigidly secured by suitable means to the left side of upper frame member 78.

Bridge 300 and cylinder 306 are movable longitudinally of the rails 56 and 57 to the left (with respect to FIG. 4) against the action of a compression spring 310.

The spring 310 is disposed about the cylinder 306 and plunger'308 with its left end bearing against upper frame member 78 and its right end bearing against bridge 300. The arrangement damps the force of carriage 54 upon return (when ratchet wheel 206 is released). A retainer 312 (FIG. 8) arranged on rail 57 limits rebound movement of cylinder 306 (to the right relative FIG. 4) as a result of decompression of spring 310 following carriage return.

Ink supply and ribbon control means 64 of the exemplary embodiment is associated with a sheave or pulley wheel 314 (FIGS. 14 and 16) which is mounted for rotation in a horizontal plane. The agency for rotation comprises a ball-bearing ring 319 having an outer race rigidly connected to the pulley wheel 314 and an inner race secured to an immobilized cylindrical bushing 318. The bushing 318 projects vertically through plate 144 and defines an axis of rotation for the pulley 314.

A radial flange 317 of the bushing 318 is rigidly secured to the upper surface of plate 144; and an internally threaded tube 316 is mounted for rotation in the bore of bushing 318. A horizontal mounting plate or flange 322 is rotatable against the upper surface of flange 317 and is tied to the tube 316 for rotation therewith by a screw 320.

Plate 322 has a plurality of vertical holes 324 adapted for receiving the plurality of pins 326 which depend from a lower horizontal flange 328 of a releaseably mounted assembly of an inking roller 330. In consequence, the inking roller 330, which, in the exemplary embodiment, is impregnated with printing ink, is rotatable above the surface of plate 144 for supplying endless ribbon 160, with ink by capillary transfer during printing.

Lineal movement of the carriage 54 during carriage spacing is translated into rotation of the inking roller 330 through the agency of a cable 360 (FIGS. 4 and 14) which has a medial portion frictionally coiled about pulley wheel 314. A left hand portion 362 (relative to FIG. 4) of the cable 360 is secured to the upper frame member 78 by a fastener 364; and a right hand portion 366 thereof is connected to one end portion of an expansion spring 368 whose opposite end portion is connected to the right side of the upper frame member 78. Thereby, upon movement of carriage 54 in opposite linear directions, pulley wheel 314 will rotate in opposite angular directions about bushing 318.

Means for transmitting pulley wheel (314) torque to the inking roller 330 during carriage spacing and correlatively for isolating the torque of pulley wheel 314 from ink roller 330 during carriage return comprises a clutch (FIGS. 14 and 17) characterized by a ratchet 370 fashioned on the lower face of flange 372 of pulley wheel 314. Pawl means 374 having a plurality of angularly spaced apart dogs 376 is rigidly secured by a fastener, herein shown as a screw 378 to tube 316 and accordingly to plate 322. In the exemplary embodiment, as carriage 54 spaces (moves incrementally to the right with respect to FIGS. 4 and 14), the pulley wheel 314 and the ratchet 370 move in the direction of arrow 380 (FIG. 17). The parts are fashioned, arranged and proportioned such that as the ratchet 370 moves in such last direction (380), clogs 376 will be in driving engagement with the ratchet 370 and accordingly plate 322 will be positively tied to pulley wheel 314 for moving inking roller 330. However, when rotation of the ratchet 370 is in an angular direction opposite arrow 380, the ratchet 370 will slip, which is to say that the dogs 376 will be cammed over the ratchet 370 by its teeth and accordingly the pulley 314 will slip and its torque will not impinge on plate 322. As a result, during carriage (54) return, the inking roller 330 will not rotate.

Inking ribbon and inking roller 330 are included in disposable cartridge 66 having a substantially rectangular plastic case 332. A plastic base 334 of the case 332 is proportioned to fit within the depending sides 335 of a transparent plastic cover 333 of said case 332. The cover 333 has a dome 352 (FIGS. 1 and 14) to accommodate sensing means 382 to be hereinafter described. The inking roller 330 and the ribbon 160 are disposed above the base 334 and within said cover 333. The base 334 has an opening 336 through which flange 322 projects to enable mounting of the inking roller 330; and it also has a plurality of perimetric upturned base flanges 337 which rigidify the base 334.

A plurality of vertical plastic ties 338 (FIGS. 15 and 16) have reduced upper end portions 344 which are rigidly secured to the top of case 332, for example, by welding or the like. Base 334 is releaseably secured to the cover 333 by ends 346 of ties 338. These ends 346 are spring-like or resilient, being split; and they are force fit through openings in base 334, and when assembled, extend beyond the lower edge 339 of cover 333. They are proportioned for force fit through aperture 345 (only one of which is shown in FIG. 15) in the mounting plate 144 for releaseably securing cartridge 66 thereto.

A pinch or pressure roller 340 (FIGS. 13 and I4) is mounted distal from platen 26 for rotation about a vertical axis member or pin 34] at one of the corners of case 332 adjacent inking roller 330. A guide roller 342 mounted at the other distal corner of the case 332 is r0- tatable about a vertical axis pin 343. A pair of route rollers 347 and 348 are mounted at opposed platen proximate corners of case 332. These last rollers 347 and 348 are rotatable about vertical plastic axis pins 349 and 350, respectively.

Ribbon 160 is trained about inking roller 330, guide roller 342, and the route rollers 347 and 348 is adapted for movement in a circuit defined thereby. Ribbon driving force is imparted by roller 330 against which the ribbon 160 is maintained in driving association by pinch roller 340.

A plastic axis member 355 (FIGS. 13 and 16) for the inking roller 330 depends from the top of cover 333 to which the axis member 355 is rigidly secured by welding or the like, said axis member 355 terminating short of base 334 and over the opening 336. Axis pins 343, and 349 are also secured to the top of cover 333 and at the opposite ends are rigidly secured to base 334 by means such as heat welding or the like. On the other hand, axis pins 341 and 350 are not secured to the cover 333. This last arrangement permits rollers 348 and 340 to be resiliently mounted for maintaining suitable tension on ribbon 160, and ribbon driving pressure on ink roller 330, respectively.

The resilient mounting is achieved by cutting base 334 away as at 351-351 (FIG. 13) to adjoining upturned flanges 337 such that a pair of resilient or flexible frame sections 353 and 354 are provided. The lower end portion of axis pin 341 is rigidly secured in an extension 356 from frame section 353; and similiarly the lower end portion of axis pin 350 is rigidly secured in a base extension 358 from frame section 354.

The parts are proportioned such that proximate course 359 (FIG. 13) of ribbon 160 may be disposed between belt 156 and the platen 26. Moreover, the entire belt 156, impactor 158 and sprocket wheel 152 are proportioned for disposition within the ribbon circuit.

For management of belt 156 for printing, a detectable member, which may be magnetically permeable, such as a soft iron slug 381 (FIGS. 12, 13, and 18), is set into belt 156 and preferably occupies a space having the same dimensions as a space taken by a die 157. Sensing means 382 for said slug 381 are supported above mounting plate 144 from inner ends of a pair of arms 384 having outer ends which are secured by fasteners such as screws 385 to said mounting plate 144. Each of a pair of substantially identical C-shaped transformer cores 386 and 387 (FIG. 18), and comprising said sensing means 382, has an identical primary welding 388 and identical secondary winding 389. The primary windings 388 are connected in parallel (FIG. 19) and to input lead means 390 of circuit 383. The secondary coils 389 are series opposing, being connected to output lead means 391 in circuit 383. The cores 386 and 387 are supported such that the opposed ends of core 387 are disposed in vertical alignment above and below belt 156, the opening between said core ends defining a sensing station 392.

As a result of the foregoing arrangement, an input from lead means 390 through coils 388 will produce like, though opposed, signals in the secondary coils 389 which will cancel and produce zero output in lead means 391, except when the belt 156 is positioned in its path such that slug 381 is disposed at station 392. This last belt position is referred to as the home position of belt 156.

OPERATION OF THE EXEMPLARY EMBODIMENT Included in circuit 383 is a code converter 394. This is fed by serial line signals over a conductor 393 to a storage of serial line signals to a parallel output. The converter 394 generates parallel signals representative of a succession of characters to be reproduced from the line signals. The code converter 394 may be of known construction and is adapted for generating for each character in succession a plural (herein six) level encoded output. Such output is imposed through parallel lead means 395 on a plural (six) level adder 396. Each condition of an up-down counter 398 represents a corresponding circuit condition of belt 156; and said updown counter 298 is adapted to generate a plural (six) level encoded output characteristic of a die 157 then in printing position or at a printing station preparatory to image transfer. Such last encoded output is imposed upon the adder 396 through parallel lead means 397 and is algebraically added (or compared) in the adder 396 with the encoded output representative of the character to be reproduced and received by the adder 396 from the code converter 394.

Only while the outputs from code converter 394 and counter 398 simultaneously are different, adder 396 will produce simultaneously a pair of operating signals through a pair of common leads 399 and 403. The operating signal through lead 399 provides (a) an input through lead 401 for conditioning the drive of motor 146 for driving and (b) an input through lead 402 conditioning counter 398 for counting. The operating signal through lead 403 is imposed on counter 398 through a lead 404 and upon a drive of motor 146 through a lead 405. The last signal is a directional and governs the direction of rotation of stepping motor drive and accordingly the direction of counting. In consequence of the directional signal, the speed with which a die 157 is aligned for printing is enhanced over a condition in which belt 156 is driveable only in one angular direction from any instantaneous position to an ensuing position.

When the encoded outputs of converter 394 and counter 398 match the operating signals through common leads 399 and 403 will cease with consequent termination of motor drive and counting. The parts are arranged such that a die 157 corresponding to a character to be reproduced then will be disposed at the printing station.

Simultaneously with a character available signal at the code converter 394 a corresponding signal is produced over a lead 406 to printing solenoid 186, said last signal being suitably synchronously delayed by known means (not shown) until a desired die 157 is aligned at the printing station. Thereupon, striker 182 (FIG. 12) will drive against follower 180 causing printing movement of impactor 158 from the dotted to the solid line position (FIG. 13) driving the selected die 157 against ribbon 160 for impactingly producing a corresponding image on a portion of web 42 then aligned with such die 157.

Also simultaneously with a character available signal, code converter 394 generates another output, synchronously delayed by means (not shown), which energizes spacing solenoid 240 through a lead 407. Ensuingly, (provided there has been no carriage return signal) pawl 208 will be rocked while in engagement with ratchet 206 to rotate shaft 204 for driving sprocket wheel 196 (FIG. 4); and accordingly, pulley belt will be driven incrementally and carriage 54 will move one space to the right (with respect to FIG. 4) against the action of restoring spring 294. Simultaneously ribbon 160 will be incrementally driven.

Code converter 394 is adapted to produce a distinctive character return encoded output over parallel lead means 395 in response to a carriage return signal. Such distinctive character return encoded output is effective for driving belt 156 to its home position (in which slug 381 is disposed at station 392). The arrangement of parts is such that when slug 381 is in such home position, counter 398 registers zero.

In response to a carriage return signal, code converter 394 generates yet another output, following a synchronous delay, by known means (not shown), the last output being imposed over a lead 408 for energizing function solenoid 246. Moreover, in a proper time sequence, in response to such carriage return signal, spacing solenoid 240 also is energized through lead 407. Resultantly, armature 251 (FIG. 10) is drawn inwardly and stripper 245 is rocked a distance sufficient to cause pawls 208 and 209 to disengage ratchet wheel 206 and prevent the related power'stroke of spacing solenoid 240 from advancing carriage 54. Instead the power of such last stroke will be shunted, through interposer 258 to lever 267 for driving pawl 270 downwardly a distance sufficient to feed web 42 downstream one line.

Should counter 398 have an output which corresponds to the home position of belt 156 following receipt of a carriage return signal, when in fact slug 381 is not disposed at home station 392, (in consequence of some malfunction) the error is attended by homing means including a conventional logic circuit 409. The logic circuit 409 receives a carriage return signal from code converter 394 by way of a lead 410. It is adapted to receive a signal from adder 396 over a wire 411, when adder 396 is in a driving mode. Upon absence of a signal in wire 411, when a carriage return signal has been received over lead 410, the logic circuit 409 will consider the nature of the output of sensor 382 over lead means 391. If such last output discloses that slug 381 is not at station 392 (as would be the fact in the presumtive situation), the logic circuit 409 will generate an output over lead 412 for driving motor 146. This driving condition will continue until the sensor output indicates that slug 381 is disposed at station 392, at which time motor driving output over lead 412 will terminate.

The logic circuit 409 is employed upon the initial setting of circuit 383. That is to say, by means (not shown) when the switch controlled by manual member 28 is moved to an on condition, a carriage return signal is generated. A chain of effects from such signal, and which have heretofore been described in connection with carriage return or line feed function, ensues, whereby the belt 156 is moved to home condition and counter 398 is set at zero.

In the event line feed is required and no carriage return signal is present in the intelligence being reproduced, carriage 54 is prevented from being overdriven by a switch 414 (FIGS. 4 and 18) which is mounted on the right side of upper frame member 78 in line with the leading end 416 of carriage 54. When this switch 414 is carriage actuated, it produces a carriage return signal in consequence of which the heretofore described carriage return chain of events occurs.

As many modifications in the described construction could be conceived, and as many widely different embodiments could be made without departing from the spirit and scope of the claims, it is intended that all matter contained in the accompanying specification shall be considered as illustrative only and not in a limiting sense.

I claim:

1. An impact printer comprising:

an endless belt disposed in a circuit and having a plurality of printing dies spaced apart longitudinally of the circuit;

impacting means mounted for successively urging said belt into a printing mode at successive printing stations;

means for moving said belt circuitously for successively aligning selected dies with said impacting means for printing;

means for translocating said belt and impacting means simultaneously to successive printing stations;

means for replaceably supporting a web coil;

means for spending the web from said coil successive line spacing distances;

a reciprocative member having a lineal power stroke;

and

means for selectively impinging force of said power stroke on said translocating means and said spending means for selectively spacing said belt and feeding said web a line at a time.

2. A printer according to claim 1 further characterized by printing ink supply means including an endless ribbon having a segment disposed adjacent said web and a die aligned for printing, and means for driving the ribbon in a circuitous path responsively to translocation of said belt and said impacting means.

3. A printer according to claim 2 wherein said translocating means comprises a carriage supportingly associated with said belt and said impacting means, said carriage having a place of beginning at the start of printing of a line of intelligence and a terminal station at end of printing of a line of intelligence, and characterized by means for returning said carriage from said terminal station to said place of beginning.

4. A printer according to claim 3 further characterized by means for disabling said driving means as said carriage returns.

5. A printer according to claim 4 characterized by a cartridge releaseably mounted on said carriage and including said ribbon and said driving means.

6. A printer according to claim 1 wherein said translocating means comprises a carriage supportively associated with said belt and said impacting means, a rotatably mounted ratchet coupleable to said power stroke for moving said carriage, and a pawl connected to said reciprocative member for rotating said ratchet, and wherein said selective impinging means includes a rockable member aligned with said pawl for disabling said translocating means.

7. A printer according to claim 6 wherein said selective impinging means also includes an interposer connected to said rockable member, said interposer having first and second positions in which said power stroke is coupled to and uncoupled from said moving means.

8. A printer according to claim 7 characterized by a solenoid operatively connected to each said reciprocative member and said rockable member.

9. A combination according to claim 1 wherein said reciprocative member has a return stroke following each lineal power stroke and characterized by:

means for increasing the force imposed on said reciprocative member as it moves through said lineal power stroke; and

means for transmitting the force of said reciprocative member to said translocating means uniformly during said lineal power stroke.

10. A combination according to claim 9 wherein said increasing means is a solenoid.

1 1. A combination according to claim 9 wherein said transmitting means comprises:

an arm having a moment coupled to said translocating means and rockable between a carriage spacing phase and a return phase; and

means for shortening the said moment as the force imposed on said reciprocative member increases.

12. A combination according to claim 11 wherein said shortening means comprises:

a lever connected to said reciprocative member and rockable responsively thereto; and

a cam arranged for movement longitudinally of said moment arm in response to rocking of said lever.

13. A combination according to claim 12 wherein said arm is mounted for rocking in a carriage spacing phase and in a return phase corresponding to the condition of said reciprocative member; and said cam is carried from said lever in sliding engagement with said arm for impinging thereon the force of said reciprocative member at the position of engagement thereof.

14. A printer comprising:

a framework having opposed lateral sides;

a carriage mounted for movement from side to side of said framework between a place of beginning and a carriage return station;

a spring connected to said carriage for tensioning upon carriage movement from said place of beginning toward said carriage return station for restoring said carriage to said place of beginning;

an endless printing belt mounted on said carriage in a circuitous path for translocation to successive printing stations and having a plurality of dies carried longitudinal of said path, said printing belt arranged for movement independently of said carriage;

means for supporting a web for image transfer adjacent said belt;

a stepping motor mounted on said carriage for driving said printing belt and aligning a selected die with the web;

an endless ribbon having a segment arranged for disposition between a selected die and the web;

a driveable sprocket wheel mounted on said framework, and a driven belt associated with said sprocket wheel for moving said carriage a space at a time from said place of beginning to said carriage return station;

means for driving the ribbon circuitously responsively to movement of said carriage a space at a time;

a first ratchet wheel associated with said sprocket wheel for moving said carriage;

a second ratchet wheel connected to said supporting means for feeding a web a line at a time;

first solenoid operated means in impacting association with said printing belt for driving each selected die into engagement with said ribbon for image transfer to said web;

second solenoid operated means drivingly associated with said first ratchet wheel for spacing said carriage following image transfer; and

third solenoid operated means for shunting the power of said second solenoid operated means away from said first ratchet wheel to said second ratchet wheel following movement of said carriage to said carriage return station.

15. A printer according to claim 14 wherein said second solenoid operated means comprises a feed pawl rockably mounted for movement through a spacing condition in which said first ratchet wheel is driven a selected angular distance for spacing said carriage and a reverse condition in which said feed paw] slips relative to said first ratchet wheel, and characterized by a check pawl having a ratchet wheel holding condition for preventing carriage return while said feed pawl is in said reverse condition and a slipping condition relative to said first ratchet wheel while said feed pawl is in said spacing condition.

16. A printer according to claim 15 wherein said second solenoid operated means also includes:

a solenoid actuated first lever;

a shaft mounted for rotation, said first ratchet wheel and said sprocket wheel mounted about said shaft; and

a link mounted about said shaft and rockably associated with said lever, said feed pawl connected to said link and rockable thereby between said spacing and reverse conditions.

17. A printer according to claim 16 wherein said third solenoid operated means comprises a solenoid actuated second lever having a stripper aligned with said feed pawl and said check pawl, and an interposer; and wherein said second lever has a first condition in which said feed pawl and check pawl are conditioned for spacing said carriage and a second condition in which said stripper prevents engagement of said first ratchet wheel and said pawls and said first lever has a striker aligned with said interposer when said second lever is in its second condition for moving said second ratchet wheel to line feed a web.

18. A printer according to claim 14 characterized by:

means for generating electrical effect according to an image to be transferred to a web;

counting means for generating output corresponding to a die aligned for image transfer; and

means for comparing said electrical effect and said output to produce a signal for driving said stepping motor until said output matches said electrical effect. 

1. An impact printer comprising: an endless belt disposed in a circuit and having a plurality of printing dies spaced apart longitudinally of the circuit; impacting means mounted for successively urging said belt into a printing mode at successive printing stations; means for moving said belt circuitously for successively aligning selected dies with said impacting means for printing; means for translocating said belt and impacting means simultaneously to successive printing stations; means for replaceably supporting a web coil; means for spending the web from said coil successive line spacing distances; a reciprocative member having a lineal power stroke; and means for selectively impinging force of said power stroke on said translocating means and said spending means for selectively spacing said belt and feeding said web a line at a time.
 2. A printer according to claim 1 further characterized by printing ink supply means including an endless ribbon having a segment disposed adjacent said web and a die aligned for printing, and means for driving the ribbon in a circuitous path responsively to translocation of said belt and said impacting means.
 3. A printer according to claim 2 wherein said translocating means comprises a carriage supportingly associated with said belt and said impacting means, said carriage having a place of beginning at the start of printing of a line of intelligence and a terminal station at end of printing of a line of intelligence, and characterized by means for returning said carriage from said terminal station to said place of beginning.
 4. A printer according to claim 3 further characterized by means for disabling said driving means as said carriage returns.
 5. A printer according to claim 4 characterized by a cartridge releaseably mounted on said carriage and including said ribbon and said driving means.
 6. A printer according to claim 1 wherein said translocating means comprises a carriage supportively associated with said belt and said impacting means, a rotatably mounted ratchet coupleable to said power stroke for moving said carriage, and a pawl connected to said reciprocative member for rotating said ratchet, and wherein said selective impinging means includes a rockable member aligned with said pawl for disabling said translocating means.
 7. A printer according to claim 6 wherein said selective impinging means also includes an interposer connected to said rockable member, said interposer having first and second positions in which said power stroke is coupled to and uncoupled from said moving means.
 8. A printer according to claim 7 characterized by a solenoid operatively connected to each said reciprocative member and said rockable member.
 9. A combination according to claim 1 wherein said reciprocative member has a return stroke following each lineal power stroke and characterized by: means for increasing the force imposed on said reciprocative member as it moves through said lineal power stroke; and means for transmitting the forcE of said reciprocative member to said translocating means uniformly during said lineal power stroke.
 10. A combination according to claim 9 wherein said increasing means is a solenoid.
 11. A combination according to claim 9 wherein said transmitting means comprises: an arm having a moment coupled to said translocating means and rockable between a carriage spacing phase and a return phase; and means for shortening the said moment as the force imposed on said reciprocative member increases.
 12. A combination according to claim 11 wherein said shortening means comprises: a lever connected to said reciprocative member and rockable responsively thereto; and a cam arranged for movement longitudinally of said moment arm in response to rocking of said lever.
 13. A combination according to claim 12 wherein said arm is mounted for rocking in a carriage spacing phase and in a return phase corresponding to the condition of said reciprocative member; and said cam is carried from said lever in sliding engagement with said arm for impinging thereon the force of said reciprocative member at the position of engagement thereof.
 14. A printer comprising: a framework having opposed lateral sides; a carriage mounted for movement from side to side of said framework between a place of beginning and a carriage return station; a spring connected to said carriage for tensioning upon carriage movement from said place of beginning toward said carriage return station for restoring said carriage to said place of beginning; an endless printing belt mounted on said carriage in a circuitous path for translocation to successive printing stations and having a plurality of dies carried longitudinal of said path, said printing belt arranged for movement independently of said carriage; means for supporting a web for image transfer adjacent said belt; a stepping motor mounted on said carriage for driving said printing belt and aligning a selected die with the web; an endless ribbon having a segment arranged for disposition between a selected die and the web; a driveable sprocket wheel mounted on said framework, and a driven belt associated with said sprocket wheel for moving said carriage a space at a time from said place of beginning to said carriage return station; means for driving the ribbon circuitously responsively to movement of said carriage a space at a time; a first ratchet wheel associated with said sprocket wheel for moving said carriage; a second ratchet wheel connected to said supporting means for feeding a web a line at a time; first solenoid operated means in impacting association with said printing belt for driving each selected die into engagement with said ribbon for image transfer to said web; second solenoid operated means drivingly associated with said first ratchet wheel for spacing said carriage following image transfer; and third solenoid operated means for shunting the power of said second solenoid operated means away from said first ratchet wheel to said second ratchet wheel following movement of said carriage to said carriage return station.
 15. A printer according to claim 14 wherein said second solenoid operated means comprises a feed pawl rockably mounted for movement through a spacing condition in which said first ratchet wheel is driven a selected angular distance for spacing said carriage and a reverse condition in which said feed pawl slips relative to said first ratchet wheel, and characterized by a check pawl having a ratchet wheel holding condition for preventing carriage return while said feed pawl is in said reverse condition and a slipping condition relative to said first ratchet wheel while said feed pawl is in said spacing condition.
 16. A printer according to claim 15 wherein said second solenoid operated means also includes: a solenoid actuated first lever; a shaft mounted for rotation, said first ratchet wheel and said sprocket wheel mounted about said shaft; and a link mounted about said shaft and rockably associated with said lever, said feed pawl connected to said link and rockable thereby between said spacing and reverse conditions.
 17. A printer according to claim 16 wherein said third solenoid operated means comprises a solenoid actuated second lever having a stripper aligned with said feed pawl and said check pawl, and an interposer; and wherein said second lever has a first condition in which said feed pawl and check pawl are conditioned for spacing said carriage and a second condition in which said stripper prevents engagement of said first ratchet wheel and said pawls and said first lever has a striker aligned with said interposer when said second lever is in its second condition for moving said second ratchet wheel to line feed a web.
 18. A printer according to claim 14 characterized by: means for generating electrical effect according to an image to be transferred to a web; counting means for generating output corresponding to a die aligned for image transfer; and means for comparing said electrical effect and said output to produce a signal for driving said stepping motor until said output matches said electrical effect. 